Duplex pumping-engine.



No. 767,612. PATENTED AUG. 16, 1904.

B. VOGEL.

DUPLEX PUMPING ENGINE.

APPLICATION FILED JAN. 31, 1903; N0 MODEL.

3 SHEETS-SHEET 1.

2/I.=-{ .22 7 l 77 r No. 767,612. I PATENTED AUG. 16, 1904.

E. VOGEL. DUPLEX PUMPING ENGINE.

APPLICATION FILED JAN. 31, 1903.

N0 MODEL. 4 5 mums-sum a.

I I I 1'9.

PA-TENTED AUG. 16, 1904.

E. VOGEL. DUPLEX PUMPING ENGINE. APPLIUATION FILED JAN. a1, 1903.

3 SHEETS-SHEET 3.

N0 MODEL.

3 gear with strong and small expansion.

UNITED STATES Patented August 16, 1904.

PATENT OFFICE.

ERNST VOGEL, OF BITTERFELD,GER1\IAN Y, ASSIGNOR TO THE FIRM OF ORTENBAOH & VOGEL, OF BITTERFELD, GERMANY.

DUPLEX PUMPING-ENGINE.

{59ECIFIGACLION forming part of Letters Patent No. 767,612, dated. August 16, 1904:.

Application filed January 81, 1903. Serial No. 141,335. No model.)

To all whom it may concern:

Be it known that I, ERNST VoenL, engineer, residing at Bitterfeld, Prussia, Germany. have invented certain new and useful Improvements 5 in Duplex Pumping-Engines; and Ido hereby declare the following to be a full, clear, and exact description of the invention, such as will enable others skilled in the art to which it appertains to make and use the same.

This invention relates to a duplex pump or engine without rotary motion in whichsteam is caused to expand. Hitherto owing to the resistance of water to the pumping action remaining uniform to the end of the stroke it 1.5 was impossible to have expansion in such pumping-engines except to a very small degree.

The pumping-engine according to this invention is illustrated in the accompanying 2 drawings, in which Figure l is a longitudinal section through one pump-cylinder as well as through the valve-chest, the valve not. being shown. Fig.

2 is a horizontal section through both the,

pump-cylinders with the steam-cylinders in plan. Fig. 3 is a cross-section through the steam-cylinders and the valve-chest. Fig.4 shows both the slide-valve surfaces in development in their central position, the cylinder- 3 faces where not visible through the openings of the valve being shown in dotted lines and the arrows indicating the direction of the movement of the valves during working. Figs. 5 and 6 show diagrammatically the valve- Fig. 7 is a cross-section through the valves in their central position on the line A A of Fig. 4. Fig. 8 is a similar section on line B B of Fig. 4; Fig. 9, a smilar section on the line C C of 4 Fig. 4; Fig. 10, a similar section on the line D D of Fig. 4. Figs. 11 and 12 show the device for altering the degree of cut-off during the working. Figs. 13, 14, 15, and 16 are developments of the valve during a double stroke that is to say, during one revolution.

The pumping-engine used is the same as that described in my patent application Serial No. 98,380, of the 15th of March, 1902. in which pump-pistons 53 54 move in two cylinders 49 50, arranged side by side and commu- 5 O nicating through passages 59 60, each of the pistons being rigidlyconnected with the steamengine pistons 2 4 by means of pistonrods 73 74 and in which instead of ordinary valves there are mounted on the piston-rods pis- 55 ton-valves 57 58, which move with the pumppistons' and open and close passages 59 60 or alternately open in one or in the other directionthat is to say, establish communication with the suction or with the discharge cham- 6O ber. As may be seen in Figs. 1 and 2, the piston-vahes 57 58 are extended and reduced in size for a certain portion of their length,

so that each of them has a thicker portion 7 5 76, moving in a correspondingly-formed 5 portion of the cylinders. The thick portions are both on the same side-zl a, toward the right-hand sidein the drawings. The areas of the piston-valves are therefore smaller on the discharge side than on the suction side, 7 the larger area being slightly larger and the smaller area slightly smaller than half the area of the pump-pistons 53 54. When the piston of one cylinder say piston 54-pumps during the movement from right to left through the opened passage 59 of the other cylinder 49, the pressure in the dischargepassage 62 at first tha't is to say, as long as the smaller portion of the piston has not arrived at its corresponding bore, or, in other words, as long as the passage 60 has not been closedacts on the full area of the pistonvalvethat is to say, on the area of the thicker portion 7 6. As soon, however, as the pistonvalve 58 enters the narrow bore the high 8 5 pressure can only act on the area of the small portion of the piston. The resistance of the pump is therefore great during the first portion of the strokethat' is to say, as long as the steam is acting with its full pressure with- 9 out expansion and small during the second or expansion period of the stroke. During the advance of the piston-that is to say, when the piston 54 pumps through the passage 59 into the dischargechamber-the pressure that acted on it originally that is to say, before the smaller portion 58 of its piston-valve came out of the small borebeeomes reduced to the valves for the two cylinders.

extent corresponding to that of the small process takes place as regards the piston 53' and its piston-valve 57 75. As during the time during which the piston-valves close the distributing-passage the adjacent pumppis' tons stand still and the space of the distributing-passages closed, in on all sides is filled completely with liquid, a further movement of the piston-valve toward the reduced bore (with reference to Fig. 1, a movement of the piston 58 from right to left) would be impossible, as the thicker portion of the piston-valve 7 6 enters the space of the distributing-passages, and therefore this space becomes re duced. In order to make it possible, each of the distributing passages or ports is provided with a valve '77, opening into the dischargespace, the displaced liquid escaping through said valves.

The valve-gear of the steam-cylinders is an expansion valve-gear with cut-off, which can be varied as desired,and there are only two These valves are rigidly connected in the well-known manner with the pistons below by means of cross arms or links connected to the valve and to the piston-rod, and therefore the valves always move exactly with the pistons, so that all the driving-gear, as well as the inoperative movement of the hitherto-lmown valve-gears, are avoided. In the accompanying drawings the valves shown are cylindrical valves; but

they may be of any other approved shape Over each cylinder there is a slide-valve rig idly connected with the piston by means of a rod 17, sothat the valve 1 makes the same movement as the piston 2 and the valve 3 the same as the piston. 4. The valve-gear is arranged in such a manner that the admission of steam to each cylinder is effected each time by both the valves, the slide-valve of one cylinder directly connected with the piston determining the end of the admission period coinciding with the beginning of compression. The slide-valve of the adjoining cylinder determines for the same cylinder the beginning of the admission and the beginning of the exhaust. In order to elfect this, the valve 1 is provided with passages 5 6 7 8 9 1O 11- 12and the slide-valve 3 with passages 13 1 1 15 16 17' 18 ,19 20 each connecting together two slotv a 0 b I like oemngs on the surface of the valve. r p

The valves 1 and 3 are further connected together by passages 21 22 23 24: 25 26 27 28.

In the construction illustrated these eight con necting-passages are partly situated in the body of the cylinders and partly in a relief or balance cover 35, which, being detachable, enables the openings of the passages to be easily machined and at the same time takes elf some of the steam-pressure on the valve. The relief of the valve is effected by the steam entering through the passage 29 on the surface of the valve into the latter. The valvechest contains, therefore, no direct live steam, or, .at the outside, only steam having the same pressure as exhaust-steam. The pressure on the cover required for obtaining tight closing of the valve could beproduced by means of springs or by a partial pressure by live steam of a smaller pressure. Live steam enters, through the passage 29, first the adjoining valve, then after having passed through an intermediate passage into the cylinder through its own cylinder-valve until the latter valve closes. Then the steam expands until the adjoining valve opens the outlet, so that the used-up steam can pass through its own valve and through another intermediate canal. This exhaustperiod is closed by the movement of the valve, which closes the passage, and thus brings about the beginning of the compression period. At the same time this steam, through another passage in its own valve and a correspondlng connectingpassage, exercises pressure on the circumference of the adjoining valve, Which in its advance movement admits live steam into the cylinder in question, so that the same operation begins over again.

The connecting and valve passages are arranged in such a manner that what has been said applies equally to the other cylinder.

With reference to the eight connecting-passages it must be also pointed out that in the arrangement shown in the accompanying :drawings, given by Way of example, the passages 21 21 25 27 always serve for the passage of live steam,and the passages 22 23 26 28 always serve for the passage of exhauststeam from one to the other cylinder. Of the passages traversing the valves the passages 6 12 15 18 are in constant communication with the exhaust 30 and the passages 5 8 17 19 with the live-steam inlet 29. The passages 6 and 12, as well as 15 and 18, are therefore con. nected together at their extremities on thevalve-surface on the side of the outlet 30 and the inlet-passages 8 and 5, as Well as 17 and 19. with the live-steam inlet 29.

The working of the distributing-gear, which may be seen in Figs. 13 to 16, is as follows: In Fig. 13 the valve 1 and the piston below it are nearing their central position. Steam enters, through the inlet 29 of the steam-cylinder, the passage 8 of the valve 1, the other end of which ,(see Fig. 10) enters the next mo- .ment into communication with the intermediate passage 24 of the cover or hood, so that .pand.

steam from the passage 24 goes through the passage 16 of the valve 3 (see Fig. 8) to the passage 33 of the steam-cylinder 46, leading to the left-hand side of the piston, so that the piston-4 is therefore driven from the left to the right. The steam in'front of this piston escapes from the passage 34, which comes from the other end of the cylinder, and goes to the face of the valve 3, where it finds the passage 20 of the said valve open, (see Fig. 7,) which passage is in communication with the intermediate passage 28 of the cover or hood. During the continued movement of the valve 1 this exhaust-steam enters the slide-valve passage 12, (see Fig. 10.) communicating with the exhaust 30. The piston 4 also has inlet on the left and outlet on the right hand side. The movement of the piston 2 in Fig. 13 takes place in such manner that live steam from the inlet 29 goes into the valve-passage 19, (see Fig. 7,) into the intermediate passage of the cover, and thence through the valve-passage 11 into the cylin der-port 31. In the position under .consideration the valve 1 is just in front of the end of this inlet, so that during its further movement it closes the passage 31, and thus the steam in the cylinder 45 begins to ex- The exhaust from the cylinder 45 takes place through the cylinder-port 32 from the right-hand side of the piston, passes through the valve-passage 7, Fig. 8, intermediate passage 23, and the valve-passage 15,

and thence enters the exhaust 30. This exhaust still remains open for some time until the passage 7 closes the cylinder-port and the compression period begins. It'will be seen from the same figure that the valve-passages 11 and 10 during a' certain period of time both communicate with the cylinder-port 31; but the steam cannot reach the exhaust through the passage 10 and through the intermediate passage, because the valve 3 completely closes the said intermediate passage 26 during the time in question and the valve-passage 18 only comes into communication with the intermediate passage 26 when the exhaust has really to take place. In Fig. 14 the first system has reached the end of its stroke, and admission takes place on the right-hand side through passages 32 9 25 17 29 and exhaust on the left-hand side through the passages 31 10 26 18 30. Admission on the left-hand side of the piston 2 takes place through the passages 33 16 24 8 29, and exhaust takes place through the passages 34 20 28 12 30. In Fig. 15 the first system is just about to reach its central position, the second system being at the end the passages 34 13 21 5 29, the exhaust taking place through the passages 32 14 22 6 30. In

Fig. 16 the piston 2 is at the left-hand 0nd of described with reference to Fig. 13.

As may be seen from Figs. 13 to 16, the

inlet and outlet passages or ports in the construction illustrated have their orifices on the cylinder-face made in such a manner that the cutting off ofv the entering and escaping steam is effected by the edges of the passages which are oblique or inclined with reference to the direction of the movement of the valve. If by means of a special device the valves are slightly moved in transverse direction to the direction of their main movement, which in case of cylindrical valves would mean a slight rotation, the degree of cut-ofi will be altered and also, if desired, that of the compression, as may be clearly seen from the figures. This transverse movement of the valve may be effected by means of a bar 40, Fig. 11, the two bent ends or pins of which, 41 42,-engage with straight longitudinal grooves 43 44 in the valve, so that the valves could be rotated only by atransverse movement of the bar 40. This transverse movement can be. effected from the ouside either by means of a screw-spindle and hand-wheel with stuffing-box, as in an ordinary valve, ,or by means of a spindle 36 with an eccentric or cam part 37, as illustrated in Figs. 3 and 12, by rotating the handle 48, Fig. 1, the rotation of the spindle through an angle of one hundred and eighty degrees altering the cut-off from the smallest to the largest extent permissible. By making the angle of the'inlet and outlet edges of difierent sizes the cut-off and the compressionwill increase more or less quickly when the valves are transversely moved to the same extent. As long as no alteratlon is made from the outslde in the cut-off of the engine the movement of thevalves is merely rectilinear, there being no transverse movement. In orderto enable the described transverse movement to be effected by hand, the valve-rods must be supported in the transverse arms 47 without any play, but rotatably.

As may be seen from the drawings, live steam enters the inlet-passage on the circumference of the valve from the cylinder and not in the usual manner from the valve-chest. In the arrangement illustrated no live steam would therefore enter the valve-chest, there being thus no steam-pressure onthe valve, as only exhaust-steam would exercise pressure on the cover or hood 35 when the valve-chest is connectcd at any point with the exhaust 30 or when steam of small tension is caused to act on the cover by means of a reducing-valve. In the event of the relief of the valve (in case only exhaust-steam is caused to act on the cover or hood) being too great and there not being suflicient pressure on the cover 35, which pressure is required for obtaininga tight joint between the valveand the cylinder-face, a portion of the live steam would enter the valvechest through the insuificiently tight joints of the valve and instantaneously produce the desired tight joint. In the latter case, however, the valve-chest must not be in communication with the exhaust 30.

What I claim as my invention, and desire to secure by Letters Patent, is

In a duplex pumping-engine, the combination, with two power-cylinders provided with pistons and piston-rods, one of the said pistons being arranged to Work half a stroke in advance of the other; of two slide-valves for the two cylinders respectively, each said slide-- valve being operated by the piston-rod of the cylinder-to which it pertains, and the said cylinders and slide-valves being provided with ports and passages arranged so that each said slide-valve operates as a main steam-distributing valve for the cylinder to which it does not pertain and as a steam-expansion valve for the cylinder to which it pertains.

In testimony whereof I aifix my signature in presence of two witnesses.

ERNST VOGEL. 

